Door clinching device



Nov. 8, 1960 H. E. DAY

DOOR CLINCHING DEVICE 2 Sheets-Sheet 1 Filed Aug. 21, 1957 INVENTOR.

Nov. 8, 1960 H. E. DAY 2,959,205

DOOR CLINCHING DEVICE Filed Aug. 21, 1957 v 2 Sheets-Sheet 2 #477 I j y.

DQOR CLINCHING DEVICE Harry E. Day, Birmingham, Mich., assignor to Delta Welder Corporation, Detroit, Micln, a corporation of Michigan Filed Aug. 21, 1957, Ser. No. 679,497

10 Claims. (Cl. 153-15) This invention relates to clamping devices, and more particularly to means for clinching together the edges of two structural members such as the inner and outer panels of an automotive vehicle door.

Most modern day automobile doors are fabricated of inner and outer panels secured together along their mating edges by clinching an outer panel flange over the edge of the inner panel. This is usually accomplished by means of a pair of dies made to conform to the shape of the door. The frequent changes in door designs which are now common in the automotive industry have made the provision of dies extremely expensive, since each new door shape has necessitated a completely new set of dies.

It is an object of the present invention to overcome the shortcomings of previously known constructions for clinching door panels or the like and to provide-a novel and improved construction which will greatly reduce the expense involved in automobile door manufacture and reduce production delays to a minimum when model changes are made.

It is another object to provide a door clinching device of this character which will greatly reduce the cost of changing the shape of an automotive vehicle door and which may be arranged as part of a group of devices for clinching various door shapes.

It is a further object to provide an improved clinching device of the above nature which may be operated by standard air pressure and may be easily handled for set-up purposes.

It is another object to provide an improved clinching device having the above characteristics, which is ofrelatively simple and foolproof construction, is easy to maintain, and may be utilized in a large variety of clinching applications.

Other objects, features and advantages of the present invention will become apparent from the subsequent description, taken in conjunction with the accompanying drawings.

In the drawings:

Figure 1 is a side elevational view of the novel clinching device of this invention, parts being broken away for clarity, and showing the device in its initial position;

Figure 2 is a view similar to Figure 1 but showing the device when the movable die has reached the end of its advancing stroke;

Figure 3 is a view similar to Figures 1 and 2 showing the device with the dies in their final closed position;

Figure 4 is a top plan view of the device shown in Figure 3;

Figure 5 is an end elevational view partly in cross sec- Figure 8 is a view similar to Figures 6 and 7 showing the flanges in clinched position.

In general terms, the device comprises a pair of diesupporting jaws connected by a linkage arrangement which may be operated by a fluid actuated device to relatively move the dies in a predetermined manner so that an upstanding flange on one panel may first be bent over and then forced down upon a flange of the second panel. The device is preferably so constructed that it may be mounted on a work table or similar support in conjunction with a plurality of additional devices of a similar nature, so that the entire rim of a door or other structural assembly may be simultaneously clinched. The jaws of each device carry dies which are removably supported thereon, andeach pair ofv dies of a group of devices may be shaped to fit a specified section of the door edge. Should it be desired to change the configuration of the clinching apparatus, one or more of a particular group of clinching devices may be replaced by other devices carrying a different die arrangement with a minimum delay in production. The clinching devices which have been removed may then be altered at leisure should a further modification of the door shape be made.

Referring more particularly to the drawings, the improved clinching device is generally indicated at 11 and comprises a first die supporting jaw 12 and a second die supporting jaw 13, these jaws supporting a pair of dies 14 and 15 respectively. Since in normal operation of the device jaw 12 will be connected to a stationary sup.- port, this jaw will be referred to as the stationary jaw while jaw 13 is termed the movable jaw. Jaws 12 and 13 may be of rectangular cross-sectional shape, and a pair of ears 16 are secured to the inner end of jaw 12 and project therefrom in parallel relation. Jaw 13 has a pin 17 fixed to its inner end, this pin extending through a pair of elongated slots 18 in ears 16. The shape of pin 17 may be such as to minimize the frictional resistance between the two jaws during their relative rocking or sliding movement, and a bearing block 19 may be provided on jaw 12 for this purpose. It will be noted that slots 18 extend parallel to jaw 12 so that the inner end of jaw 13 is confined to movement in this direction;

The outer ends of jaws 12 and 13 are provided with enlarged portions 21 and 22 respectively, having facing recesses in which are removably secured a stationary die 14 and a movable die 15. These dies are mounted on their respective supporting jaws 12' and 13 by any appropriate means such as bolts 23. The working portions of dies 14 and 15 have complementary configurations as seen best in Figure 5, the facing surfaces of the dies conforming to a predetermined portion of a door edge shape or other structural units which are to be formed. In the particular illustration, dies 14 and 15 have a doubly curved shape which is common to the upper edges of rear doors in several commonly known American cars. Adjacent units 11 could carry pairs of dies adapted to clinch adjacent portions of the doors edge. Such dies are indicated in dot-dash lines at 24 and 25. When arranged in this manner, adjacent units 11 may be mounted on a table or similar support so that the work may be conveniently applied to the units.

The linkage means which connects jaws 12 and 13 functions to control the movement of dies 14 and 15 in such a manner that, starting with the position in Figure 1, die 15 will first move to the left with respect to die 14 and will then move downwardly with respect to die 14. For this purpose, the linkage means includes a fixed arm 26 extending from the inner end of stationary jaw 12 and an L-shaped arm 27 one leg of which is pivoted at 28 to the outer end of jaw 12. A cylinder 29 is pivoted at 31 to the outer end of arm 26 and piston rod 32 of this cylinder is pivoted at 33 to the outer end of arm 27. Cylinder 29 is a double acting cylinder which is connected by conduits 34 and 35 to a fluid pressure system such as a standard compressed air system found in manufacturing establishments. It will be seen that leftward movement of piston rod 32 as seen in Figure 1 will result in clockwise movement of arm 27 about pivot 28, whereas retracting movement of piston rod 32 will cause counterclockwise rotation of arm 27.

Means are connected to arm .27 for accomplishing both the leftward and downward movements of die as seen in Figure l. The leftward movement of die 15, which could be termed the folding stroke'since it would normally cause the flange of one panel to be partially bent or folded over the other, is accomplished by a link 36 pivoted at 37 to the outer leg of arm 27 and at 38 to a crank arm 39 of a cam 41, this cam being pivoted at 42 to jaw 12. More specifically, jaw 12 is provided with an elongated clearance aperture 43 within which cam 41 is pivotally supported. The cam has a forwardly facing recess 44 disposed between a projecting ear 45 and a convex lobe 46, the cam swinging in a plane parallel to the extent of the jaws. The main portion of lobe 46 is concentric with pivot 42, and the lower end of cam 41 is depressed as indicated at 47.

Pivoted at 48 forwardly of cam 41 within cut-out 43 is a bell crank 49, one arm of this bell crank being engageable with cam 41 and having an outer end 50 with a concave curvature'complementary to lobe 46. The other arm of bell crank 49 has a rounded outer end projecting upwardly into a bushing 51 inserted in a counterbore on the underside of jaw 13. With this arrangement, it will be seen that when arm 27 is rotated clockwise from its position in Figure l, cam 41 will be also rotated clockwise and will cause counterclockwise rotation of bell crank 49, since the upper portion of lobe 46 of cam 41 will engage this bell crank. Thus, jaw 13 will slide leftwardly in Figure 1 with respect to jaw 12. When the main portion of lobe 46 reaches the bell crank arm, outer end 56 of this arm will ride on the lobe with no further bell crank rotation. A clearance recess 52 is provided in the underside of jaw 13 to accommodate the upper portion of cam 41 as the latter rotates clockwise from its position of Figure l.

A button 53 is mounted on the underside of movable jaw 13 adjacent the outer end thereof, this button being urged against jaw 12 by a spring 54 mounted between jaw 13 and button 53. A plate 55 is mounted on jaw 13 and serves to guide button 53. The outer position of jaw 13 with respect to jaw 12 is determined by a guard 56 of inverted U-shape which is secured to jaw 12 at an intermediate portion thereof and extends around jaw 13. A button 57 is secured to the upper surface of jaw 13 and engages the central portion of bracket 56 so that the outer limiting position of jaw 13 with respect to jaw 12 will be as seen in Figure 1. This position is such that a space will be provided between the facing surfaces of dies 14 and 15 which is sufficient to accommodate the parts during the clinching operation.

The means for drawing dies 14 and 15 together after die 15 has been moved to the left with respect to die 14, as seen in Figure 1, comprises a link 58 in the form of a rectangularly looped member which is pivotally connected at 59 to the inner leg of arm 27 and has a one-Way or lost motion connection with the outer end of jaw 13 in a direction transverse to the extent of the jaw. As seen in Figure l, the spacing of pivot 59 from pivot 28 is such that, when arm 27 is swung clockwise from the position of Figure l, pivot 59 will have a downward as well as a leftward component of movement which will draw the upper end of link 58 downwardly. The upper end of link 58 has a projection 61 disposed within a recess 62 in a block 63 mounted on the outer end of jaw 13. When the parts are in the position shown in Figure 1, a space exists between projection 61 and the bottom of recess 62, so that link 58 may travel a predetermined distance before engaging block 63. Further clockwise movement of arm 27, that is, from the position shown in Figure 2 to that shown in Figure 3, will result in jaw 13 being drawn downwardly against jaw 12, with the result that die 15 will be forced toward die 14. It should be noted that during this latter phase of the movement the upper end of lobe 46 on cam 41 will have passed bell crank 49 so that no further leftward movement of jaw 13 will occur.

in the illustrated embodiment of the invention, means are provided for preventing undue shearing stresses on pivot pins 28 and 59. More specifically, arm 27 has concave bearing blocks 64 and 65 carried thereby adjacent pivots 28 and 59 respectively, these blocks being retained in position by members 66 and 67 secured to arm 27. Projecting from the underside of jaw 12 is a journal block 68 which rests within bearing block 64. Similarly, the lower portion of link 58 has a journal block 69 which interfits with bearing block 65, as seen in Figures 2 and 5. Pin 59 passes through block 69 and an ear 71 projecting from an intermediate portion of block 65, as seen in Figure 5. A similar arrangement is provided for the connection between blocks 64 and 68. In this manner, it will be seen that the compressive forces exerted on arm 27 between pins 28 and 59 when arm 27 is rotated clockwise from its position shown in Figure 1 will be spread over a relatively large area and that pins 28 and 59 will not be subject to excessive shearing stresses.

Operation The functioning of the apparatus described above may perhaps best be understood by a description of the movements of the parts during a normal clinching operation. To aid in this description, Figures 6, 7 and 8 are provided to show the manner in which the dies act upon a pair of panels being secured. More specifically, Figures 6, 7 and 8 are intended to correspond to the positions shown in Figures 1, 2 and 3 respectively.

As illustrated, the panels to be secured comprise a first panel 72 and a second panel 73. Panel 72 may be the outer panel of an automobile door whereas panel 73 is the inner panel of such door. Initially, panel 72 is provided with an upstanding flange 74 whereas panel 73 is provided with a flange 75 adapted to rest flush against panel 72 adjacent its flange 74. With the parts in this position, as seen in Figure 6, the edge of panel 72 may be placed on the exposed outer surface of stationary die 14 with its flange 74 in the path of movable die 15. The spacing between dies 14 and 15 is suflflciently great to permit flange 74 to be bent over flange 75 when die 15 is moved to the left.

Assuming that unit 11 shown in the drawing is one of a group mounted on a table so as to surround a door or similar object the panels of which are being clinched, cylinders 29 of these units will be simultaneously pressurized to extend piston rods 32. This will cause arm 27 of each unit 11 to be rocked clockwise in Figure 1, drawing link 36 downwardly and to the .left and thus rotating cam 41 clockwise about pivot 42. Since bell crank 49 is engaged in recess 44 of cam 41, the bell crank will be swung counterclockwise, moving jaw 13 to the left in Figure 1. Meanwhile, as pivot 59 is swung about pivot 28, link 58 will be drawn downwardly, taking up the space between projection 61 and block 63.

As die 15 moves to the left as seen in Figure 6, it will engage flange 74 of panel 72, bending this flange over flange 75 of panel '73 as seen in Figure 7. As the lower portion of lobe 46 begins to slide past curved surface 50 of bell crank 49, jaw 13 will stop its leftward movement. At the same time, the further downward movement of link 58 will cause the outer end of jaw 13 to move downwardly toward jaw 12 through the engagement of projection 61 with block 63. This will cause die 15 to move downwardly, compressing flange 74 against flange 75 as seen in Figure 8. The forces acting on the pivotal link. connections during this movement will be spread over relatively large areas because of the presence of bearing blocks 64 and 65 as well as the rounded configuration of projection 61 which engages concave recess 62 of block 63. The final position of unit 11 is shown in Figure 3.

When it is desired to retract the dies in order to remove the clinched panels, piston rod 32 will be retracted, causing counterclockwise rotation of arm 27 about pivot 28. Initially, this will cause lifting of link 58, permitting spring 61 to spread apart jaws 12 and 13 and attached dies 14 and 15. Further counterclockwise movement of arm 27 will cause ear 45 on cam 41 to engage bell crank 49, rocking the bell crank clockwise and thus moving jaw 13 to the right with respect to jaw 12. The parts will finally arrive in their initial position as shown in Figure 1, after which the panels may be removed.

It should be noted that during the clamping movement of the jaws, that is, from the position shown in Figure 2 to that shown in Figure 3, die 15 will move almost directly downwardly, there being a slight curvature to the movement due to the rocking of jaw 13 about pin 17. However, the length of jaws 12 and 13 relative to the transverse movement of die 15 is so great that the curvature of this motion will be negligible.

It will thus be seen that an extremely versatile type of clamping device has been provided which is usable for clinching door panels as well as many other types of structures. Because of the relatively small size of the device it may be used as part of a group of similar devices arranged in series so that a complete structure such as a vehicle door may be simultaneously clinched. Since each pair of dies is applied only to a relatively small portion of a larger structure, the dies may be inexpensively replaced when changes in shape are required.

While it will be apparent that the preferred embodiment of the invention disclosed is well calculated to fulfill the objects above stated, it will be appreciated that the invention is susceptible to modification, variation and change without departing from the proper scope or fair meaning of the subjoined claims.

What is claimed is:

1. In a device for clinching an upstanding panel flange over a second panel flange, a first stationary jaw having inner and outer ends, a second movable jaw having inner and outer ends, said jaws comprising elongated members in facing relation, means slidably and pivotally connecting the inner ends of said jaws to each other, means for removably securing a pair of mating dies to the outer ends of said jaws, the jaws having a normal position in which said first jaw protrudes from said second jaw, whereby said panel flanges may rest on said first jaw with the upstanding panel flange in the path of said second jaw, yieldable means for holding the outer ends of said jaws spaced apart a predetermined distance, first actuating means for moving said movable jaw outwardly in a direction substantially parallel to said stationary jaw, whereby said upstanding panel flange will be bent over said second panel flange, and second actuating means for moving the outer end of said movable jaw toward said stationary jaw against the action of said yieldable means, whereby said upstanding panel flange will be compressed over said second panel flange.

2. In a device for folding and clinching an upstanding panel flange against a second panel flange, first and second elongated jaws in facing relation and having inner and outer ends, means slidably and pivotally connecting the inner ends of said jaws, means for mounting complementary dies on the outer ends of said jaws, the jaws having a first position in which said dies are spaced apart a predetermined distance and the die on said first jaw projects outwardly from the die on said second jaw, whereby said panel flanges may rest on said first jaw with the upstanding panel flange in the path of said second jaw, a reciprocating actuator, means responsive to movement of said actuator in one direction for moving said jaws to a second position in which said dies are still spaced apart said predetermined distance but the die on said second jaw is moved outwardly, whereby said upstanding flange will be bent over said second flange, and means for moving said jaws from said second position to a third position in which the die on said second jaw is moved closer to the die on said first jaw, whereby said upstanding flange will be compressed against said second flange.

3. In a device for bending and clinching an upstanding panel flange against a second panel flange, a first elongated jaw having inner and outer ends, a first die secured to the outer end of said first jaw, a second elongated jaw having inner and outer ends, a second die secured to said second jaw and complementary to said first die, means slidably and pivotally connecting the inner ends of said jaws, the jaws being movable between a first position in which said dies are spaced apart a predetermined distance and said first die projects outwardly from said second die, a secondposition in which said second die is advanced outwardly with respect to said first position, and a third position in which said second die is brought closer to said first die than in said first and second positions, an arm fixed to said first jaw at the inner end thereof and projecting laterally therefrom, a second arm pivotally secured to said first jaw adjacent the outer end thereof, a reciprocable actuator connected between the outer ends of said arms, first linkage means connected between said second arm and said second jaw for moving said second jaw from its first to its second positions when said second arm is swung in one direction by said actuator, and second linkage means connected between said second arm and said second jaw for moving said second jaw from its second to its third position upon further movement of said second arm in said one direction by said actuator, said second linkage means being ineffective to move said second jaw during the first portion of said second arm movement.

4. The combination according to claim 3, said first linkage means comprising a cam pivotally mounted on an intermediate portion of said first jaw, a link connecting said cam to said second arm, and a bell crank pivotally mounted on said first jaw and having a first portion engageable with said cam and a second portion engageable with said second jaw, the shape of said cam being such that initial rotation of said cam will cause rotation of said bell crank and continued rotation of said cam will cause said cam to slide past said bell crank.

5. The combination according to claim 3, said second linkage means comprising a link pivoted to said second arm at a point spaced a substantial distance from the pivot between said second arm and said first jaw, and a lost motion connection between said link and said second jaw, initial movement of said second arm in said one direction causing said lost motion to be taken up, continued movement of said second arm in said one direction causing said link to move said second jaw toward said first jaw.

6. In a device for bending and clinching an upstanding panel flange over a second panel flange, first and second elongated jaws, a slidable and pivotal connection between the inner ends of said jaws, means on said first jaw for supporting a first die, means on said second jaw for supporting a second die, said second jaw being movable between a first position in which said first die projects outwardly from said second die, a second position in which said second die is advanced outwardly with respect to its first position, and a third position in which said second die is moved toward said first die, an arm fixed to and projecting laterally from the inner end of said first jaw, a second arm pivoted tosaid first jaw adjacent the outer end thereof, a piston and cylinder connected between said arms, a cam pivoted on said first jaw, a link connecting said cam and said second arm, a bell crank pivoted on said first jaw and having a first portion engage 7 able with said cam and a second portion engageable with said second jaw, said cam being so shaped that initial rotation of said second arm in one direction will cause said bell crank to move said second jaw from its first to its second positions and continued rotation of said second arm will cause idling movement of said cam, a second link pivoted to said second arm at a point spaced from the pivot between said second arm and first jaw, a lost motion connection between said second link and the outer end of said second jaw, whereby initial movement of said second arm in one direction will cause said lost motion to be taken up and continued rotation of said second arm will cause said second link to draw said second jaw toward said first jaw, a spring urging said jaws apart, and a projection on said cam engageable with said bell crank when said second arm is rotated in the opposite direction to retract said second jaw to its first position.

7. The combination according to claim 6, said second link comprising a rectangularly looped member, one end section of said member being pivoted to said second arm, the other end section of said member having a rounded projection, and a concavely recessed block on said second jaw for receiving said projection.

8. The combination according to claim 6, further provided with a rounded button on the side of said second jaw facing said first jaw, said spring urging said button against said first jaw, and a bracket secured to said first jaw and overlying an intermediate portion of said second jaw to limit the outward movement of said second jaw with respect to said first jaw.

9. The combination according to claim 6, the pivotal connections between said second arm and said first jaw and second link respectively comprising bearing blocks secured to said second arm and journal blocks secured to said first jaw and second link, whereby the compressive forces acting between said pivots will be transmitted substantially through said blocks.

10. The combination according to claim 6, provided with an elongated clearance aperture in said first jaw, said cam and bell crank being pivoted within said clearance aperture, a second aperture in said second jaw for receiving said second portion of said bell crank, and a clearance recess in said second jaw for accommodating said cam.

References Cited in the file of this patent UNITED STATES PATENTS 

